CN103527279A

CN103527279A - Oscillating motor adjuster with a hydraulic valve

Info

Publication number: CN103527279A
Application number: CN201310280869.1A
Authority: CN
Inventors: 安德烈亚斯·克内希
Original assignee: Hilite Germany GmbH
Current assignee: Hilite Germany GmbH
Priority date: 2012-07-06
Filing date: 2013-07-05
Publication date: 2014-01-22
Anticipated expiration: 2033-07-05
Also published as: EP2870327A1; JP6176656B2; JP2014016031A; WO2014006056A1; EP2870327B1; DE102012106096B3; US9322418B2; US20140157980A1; CN103527279B

Abstract

The invention relates to an oscillating motor adjuster with a hydraulic valve. Said hydraulic valve has a stepped bore with working connections outgoing therefrom. A pressure-equalised hollow piston is axially movable within the bore. With a first outer diameter, said hollow piston can be moved within a bore section so as to have a toleranced sealing ability. Following this first outer diameter, the hollow piston has - an adjacent lateral surface with a large outer diameter in the axial regions of the one working connection and - a lateral surface with a small outer diameter in the region of the other working connection. A leading edge and a trailing edge exit each of the two lateral surfaces. The two leading edges face away from each other. The trailing edges face towards each other, and therefore a supply pressure admitted into a hollow space of the hollow piston is present on one side on a projected circular surface. Said circular surface is formed from the small outer diameter, and therefore a force is effective in an axial direction. In contrast, the supply pressure on the other side is present on a projected ring surface. Said ring surface is formed from the large outer diameter minus the first outer diameter. The hollow piston is pressure-equalised due to the circular surface being equal to the ring surface.

Description

Rotary actuator with hydrovalve

Technical field

The present invention relates to a kind of rotary actuator with hydrovalve.

Background technique

By the known a kind of hydrovalve for rotary actuator of DE10 2,005 041 393A1.This hydrovalve is consistent with the present invention has the piston being arranged in longitudinal movement in hole.From the inwall of valve, sent

-pressure medium interface P and

Axially directly follow working interface A and the B of this pressure medium interface for-two.Pressure chamber's flow pass that piston has pressure chamber's flow channel and arranges dividually with this flow channel.In a kind of design proposal that is about to mention, piston can be manufactured by composite or with powder metallurgy injection moulding process equally.At this, enumerated as an example metal injection moulding.

DE196 37 174A1 show a kind of hydrovalve for rotary actuator, and wherein piston is arranged in the hole with longitudinal axis with longitudinal movement.From the inwall in hole, two working interface A, B and a pressure medium interface P have been sent.At this, pressure medium interface P is disposed axially between two working interface A, B.

By the same known a kind of hydrovalve for rotary actuator of DE198 53 670B4.From the inwall in hole, two working interface A, B and a fuel-tank outlet T have been sent.At this, fuel-tank outlet T is disposed axially between two working interface A, B.The pressure medium interface P that is arranged in the distolateral place of hydrovalve flows to hole or inner box type piston by pressure.

Hydrovalve by the known another kind of DE10 2,004 038 252A1 for rotary actuator.From the inwall in hole, pressure medium interface P, fuel-tank outlet T and two working interface A, B have axially been sent successively.

Summary of the invention

Task of the present invention is, creates a kind of rotary actuator with hydrovalve, and its pressure medium interface P is axially adjacent with two working interface A, B in common side.

According to an advantage of the present invention, pressure medium interface P directly follows the first working interface A (B).This first working interface A directly or indirectly follows the second working interface B (A)." indirectly " mean to also have a fuel-tank outlet T can be between two working interface A, B.Due to the direct or indirect adjacent layout of two working interface A, B, in for example relatively rotating final controlling element and be arranged in the situation of hydrovalve at center, rotary actuator can axially correspondingly be implemented long and narrowly.At this, the name of two working interface A and B is arbitrarily.

According to another advantage of the present invention, pressure medium interface P is disposed axially in after two working interface A, B or before.Therefore, this pressure medium interface P can outside rotary actuator, be coupled in hydrovalve, supply pressure can be delivered to the passage place of working interface A or B by fluid delivery pump.Therefore, hole in rotary actuator, that supply pressure is guided to the pressure medium interface P in rotary actuator by fluid delivery pump is optional.The hole of especially passing the rotor of rotary actuator has like this been improved processing cost and has weakened rotor.In particularly advantageous mode, so hydraulic fluid is conducted through the box type piston of valve.

Hydrovalve has shoulder hole, and this shoulder hole has working interface A, the B sending from this shoulder hole.In this hole, by pressure balanced box type piston, can be moved axially.Box type piston sealably moves in bore section with the first outer diameter under certain tolerance.Box type piston is followed this first outer diameter and is adjacent to have

-therein in the axial region of a working interface with the enveloping surface of large outer diameter and

-in the region of other working interface with the enveloping surface of little outer diameter.Each inflow seamed edge and an outflow seamed edge send from two enveloping surfaces.Two flow into seamed edges and deviate from each other and point to.Flow out seamed edge and point to relative to one another, thereby make to be introduced in the disc place that supply pressure in the cavity of box type piston is carried in projection on the one hand.This disc is formed by little outer diameter, thereby makes capablely to work in the axial direction.In contrast, supply pressure is carried in the anchor ring place of projection on the other hand.This anchor ring is deducted the first outer diameter by larger outer diameter and is formed.

By making disc equal anchor ring, box type piston is by pressure balance.

In order to reach accurate pressure balance, these faces are in concrete ratio each other.Via area formula of circle, draw three attached outer diameter D1, D2, D3 of piston:

D1=4×K

D2=5×K

D3=3×K

At this, K is constant arbitrarily.Outer diameter D1 is little outer diameter.Outer diameter D2 is large outer diameter.Outer diameter D3 is the first outer diameter.Therefore, above-mentioned anchor ring is formed by the disc product moment at two outer diameter D2, D3 place.

Except two working interface A, B, can be provided with equally one or two bypass interface A1, B1.With this, realize according to a kind of method of DE10 2,006 012 733A1, it makes the hydraulic fluid that flows to fuel-tank outlet can supply rotary actuator for pivot movement by means of safety check.

Hydrovalve must be as the hydrovalve radial arrangement at center in rotary actuator.Substitute pressure medium interface P is arranged between working interface A, B, pressure medium interface P is disposed axially in to working interface A, B side and also in the situation outside or acentric layout of hydrovalve, brings advantage.In the situation of so outside layout, hydrovalve is for example fixed on

-cylinder head,

-cylinder cover,

-dividing plate between cylinder head and rotary actuator or partition or

-be arranged in rotary actuator cover before.Use in the situation of acentric layout is particularly advantageous, and this is because acentric hydrovalve has the electromagnetic adjusting element that is attached to regularly hydrovalve place conventionally.Such electromagnetic adjusting element has by pressure balanced magnetic armature.For pressure balance, magnetic armature has the recess of the space that is connected to before magnetic armature and space after magnetic armature.Magnetic armature moves in the armature inner chamber at fuel-tank outlet place that is connected in hydrovalve.Because there is no conclusive pressure from this fuel-tank outlet, so space does not have pressure and adjusts element and do not push open from hydrovalve.Relatively, the hydrovalve two axial ends with supply interface for example applies with supply pressure to space with the order of P-B-T-A-P, thereby make to adjust element and hydrovalve, is deviated from each other and presses.Therefore, the mode of execution as acentric hydrovalve according to the present invention combines following advantage:

The axially shorter structure space of-hydrovalve and

The connection that there is no power of-adjustment element.

Box type piston is directed axially in shoulder hole.This hole can particularly advantageous mode be added in the lining of cartridge valve.Yet hole can be arranged in housing equally.In a kind of particularly advantageous mode of execution, hole is directly added in centre bolt, and this centre bolt screws the rotor of rotary actuator and camshaft.

Accompanying drawing explanation

By three embodiments, the present invention is elaborated below.

Wherein:

Fig. 1 shows rotary actuator with cross section graphic form,

Fig. 2 shows a kind of electromagnetic adjusting element that obtains the hydrovalve of use in rotary actuator with cross section graphic form, and

Fig. 3 shows a kind of hydrovalve that obtains use in the situation of rotary actuator with cross section graphic form.

Embodiment

Utilization is according to the rotary actuator 14 of Fig. 1, at the run duration of internal-combustion engine, in the angular orientation of the camshaft 18 relative driving wheels 2 in place, infinitely changed.By the torsion of camshaft 18, the start-up time of scavenging air valve and close moment are so converted, that is, internal-combustion engine brings its best power in every speed.Rotary actuator 14 has columniform stator 1, and it is connected with driving wheel 2 in anti-relative rotation.In this embodiment, driving wheel 2 is the sprocket wheels via the chain not being shown specifically of its guiding.Yet driving wheel 2 can be toothed belt wheel equally, drive belt directed via it as driving element.Via this driving element and driving wheel 2, stator 1 is connected with crank-driven.

Stator 1 comprises columniform stator matrix 3, on stator matrix inner side, radially inwardly equally spaced stretches out contact pin 4.Between adjacent contact pin 4, be formed with gap 5, via the hydrovalve 12 at the center that is arranged in being shown specifically, control ground in Fig. 2, pressure medium is brought in this gap.Between adjacent contact pin 4, erect and have blade 6, its columniform rotor hub 7 radially outwards from rotor 8 stretch out.This blade 6 is correspondingly divided into Liang Ge

pressure chamber

9 and 10 by the gap between contact pin 45.The controlling device of attaching troops to a unit in the direction " doing sth. in advance " in one of them pressure chamber 9, in contrast another pressure chamber controlling device in the direction in " delay " of attaching troops to a unit.

Contact pin 4 is with on its distolateral outer enveloping surface that abuts in hermetically rotor hub 7.Aspect blade, blade 6 is with on its distolateral columniform inwall that abuts in hermetically stator matrix 3.

Rotor 8 is connected with camshaft 18 in anti-relative rotation.In order to change the angular orientation between camshaft 18 and driving wheel 2, rotor 8 is rotated with respect to stator 1.For this reason, the pressure medium according to the sense of rotation of expectation in

pressure chamber

9 or 10 is placed under pressure, and correspondingly another

pressure chamber

10 or 9 is unloaded to fuel tank T.For rotor 8 relative stator 1 are pivoted in the position illustrating widdershins, the first rotor passage 19 of the ring-type in rotor hub 7 is placed under pressure by hydrovalve 12.By this first rotor passage 19, so other passage 11 leads in pressure chamber 10.This first rotor passage 19 is attached troops to a unit in the first working interface A.For pivotable rotor 8 deasil in contrast, the second rotor channel 20 of the ring-type in rotor hub 7 is placed under pressure by hydrovalve 12, leads in passage 13.This second rotor channel 20 is attached troops to a unit in the second working interface B.These two rotor channels 19,20 axially arrange at each interval about medial axis 22, thereby make it, in the figure plane of Fig. 1, mulched ground is stacked each other.

Rotary actuator 14 is placed on the assembled cam shaft 18 that is implemented as hollow tubular 16.For this reason, rotor 8 is inserted on camshaft 18.Hollow tubular 16 has hole 23,24, its by attach troops to a unit in the rotor channel 19,20 of two working interface A, B hydraulically with lining 27 at hydrovalve 12 in

transverse holes

25,26 connect.

Therefore, rotary actuator 14 can swing by means of visible hydrovalve 12 in Fig. 2.

In the hole 28 at lining 27Nei center, have two different internal diameters 29,30, these two different internal diameters are via the mutual transition of conical bore region 31.The first transverse holes 25 of lining 27 is sent and therefore attaches troops to a unit in the first working interface A from larger internal diameter 29.The second transverse holes 26 of lining 27 is sent and therefore attaches troops to a unit in the second working interface B from less internal diameter 30.In lining 27, box type piston 32 is removable.For this reason, box type piston 32 have distolateral this box type piston of end, for the abutment face 33 of electromagnetic adjusting element 34.The tappet 35 of electromagnetic adjusting element 34 abuts in this abutment face 33 in centre.In another distolateral end, helical compression spring 36 abuts in box type piston 32 places, and this helical compression spring is supported on the supporting member place of lining 27.At this, helical compression spring 36 abuts on the end ring face 81 of box type piston 32.Therefore, box type piston 32 can axially move relative to lining 27 with the spring force that electromagnetic adjusting element 34 overcomes helical compression spring 36.Box type piston 32 has flow channel 37 and flow pass 38.Flow channel 37 is in the cavity 80 in box type piston 32 and via the hole 28 at center, in the region of little internal diameter 30, to lead to the pressure medium interface P being axially introduced in lining 27.In contrast, flow pass 38 leads to fuel-tank outlet T.Flow channel 37 is realized via the wall extending obliquely haply 40 in box type piston 32 with the description of flow pass 38.The extension part of this inclination is controlled seamed edge by four and is opened for 41,42,43,44 minutes.These are controlled

seamed edge

41,42,43,44 and are arranged in the annular tab 45,46 that radially deviates from box type piston 32 ground extensions.Two axial each intervals of annular tab 45,46.The close annular tab 45 of adjusting element 34 has in the hole 28 with the enveloping surface 47，Qie center of large outer diameter D2 directed in the region of larger internal diameter 29.Away from the annular tab 46 of adjusting element 34, have in the hole 28 with the enveloping surface 48Qie center of little outer diameter D1 directed in the region of little internal diameter 30.Control the side facing with each other that

seamed edge

42,43 defines annular tab 45,46 for two.Two other control

seamed edges

41,44 define the side deviating from each other of annular tab 45,46.

Flow pass 38 leads to fuel-tank outlet T by two control seamed edges that face with each other 42,43.In contrast, flow channel 37 leads to two control seamed edges that deviate from each other 41,44.Therefore, two control seamed edges that face with each other 42,43 form and flow out seamed edge, and the control

seamed edge

41,44 deviating from each other in contrast forms and flows into seamed edge.

In the cut-off neutral position shown in Fig. 2 of hydrovalve 12, two control seamed edges that face with each other 42,43 have the relatively

large coincidence part

50,51 with lining 27.In contrast, in this cut-off neutral position of hydrovalve 12, two control seamed edges that deviate from each other 41,44 do not have the coincidence part with lining 27.Therefore according to the principle that flows out seamed edge control, guaranteed as follows, that is, rotor 8 relative stator 1 are compacted in definite angular orientation.The principle that flows out seamed edge control is elaborated in DE198 23 619A1.

The first outer diameter D3 of box type piston 32 sealably moves in bore section 71 under certain tolerance.This bore section 71 is formed by sleeve pipe 64, and itself and lining 27 are permanently connected.For this reason, sleeve pipe 64 is pressed in lining 27.The first outer diameter D3 of box type piston 32 conforms to the first internal diameter 70 of sleeve pipe 64 haply.The first outer diameter D3 is being followed by the axial direction of pointing to of pressure medium interface P by adjusting element 34

-therein in the region of a working interface A with enveloping surface 47 Hes of large outer diameter D2

-in the region of other working interface B with the enveloping surface 48 of less outer diameter.

Box type piston 32 in particularly advantageous mode by pressure balance, thereby the position regulation of rotary actuator 14 can be implemented high-qualityly.For this reason, the axial force being applied on box type piston 32 is cancelled out each other.That is to say the supply pressure not relying on pressure medium interface P, the power F2 that the power F1 of effect equals to act in the accompanying drawings left to the right.

The supply pressure being introduced in the flow channel 37 of box type piston 32 from pressure medium interface P is carried on the disc 60 of projection in whole plane on the one hand.This disc 60 is formed by the less outer diameter D1 of box type piston 32.Disc 60 is projected in the plane perpendicular to medial axis 22 by the wall 40 of end ring face 81 and extension obliquely.Therefore form and be applied to the power F1 adjusting on element 34.Contrary power F2 acts on anchor ring 61 via supply pressure, and this anchor ring is formed by the anchor ring 99 of anchor ring 83 deductions at the first outer diameter D3 place at the outer diameter D2 place large.As visible in second figure of Fig. 2, by this difference, formed as projecting to the anchor ring 61 perpendicular to the face in the plane of medial axis 22.

The less internal diameter 30 of lining 27 conforms to the little outer diameter D1 at enveloping surface 48 places haply.Therefore, little outer diameter D1 has defined disc 60 haply, and it has multiplied each other given in advance in the axial direction with the pressure at pressure medium interface P place, the power F1 acting on left in the accompanying drawings.The power F2 working is in the opposite direction determined by anchor ring 61, the distolateral 63 places formation of the sleeve pipe 64 of this anchor ring in being pressed into lining 27.This distolateral 63 distolateral 62 opposed with annular tab 45.

Therefore, flow channel 37 has been set up the hydraulic connecting between disc 60 and anchor ring 61.The size that disc 60 and anchor ring 61 are identical for pressure balance has.Therefore reach without any power, it makes to adjust element regulation position and especially in the neutral position illustrating, becomes easy.By this neutral position or cut-off neutral position, be conditioned.

From cut-off neutral position out and turn back to the clockwise or counterclockwise pivotable rotor 8 of of short duration light exercise wherein.

Figure 2 illustrates interface order or port order P-B-A-T.Therefore be followed successively by:

-pressure medium interface P,

-one of them working interface B,

-other working interface A and last

-fuel-tank outlet T.

At this, the conveying of supply interface P axially realizes.

Two kinds of other alternative possibilities of interface also shown in broken lines in Fig. 2.Therefore, substitute fuel-tank outlet T, be embodied as fuel-tank outlet T1 to the outlet of fuel tank.At this, fuel-tank outlet T1 is disposed axially between two working interface A, B.In this case, the flow pass 38 to fuel-tank outlet T can be closed according to dotted line 87 equally.

Following alternative is also possible,, radially settles as follows axial interface that is, that is, recess is arranged in lining or in box type piston 32.This illustrates by supply interface P1 or fuel-tank outlet T3.

In a kind of alternative design proposal, convex shoulder is not realized with sleeve pipe 64.As an alternative another design proposal can be set, utilize this design proposal can realize assembling capacity.For example, lining 27 is embodied as two-piece type and is screwed around member together, and this is as the alternative convex shoulder with single type of sleeve pipe 64.So screw plane, guaranteed assembling capacity.

As substituting of lining, equally hole can be set in housing.

In a kind of alternative design proposal, pressure medium interface P is not axially incorporated in lining 27.As an alternative, pressure medium interface P is radially introduced.For this reason, for example transverse holes or recess can be arranged in the wall of lining 27.So this transverse holes is in the axial region of helical compression spring 36.

Hydrovalve can be implemented as the hydrovalve at center according to this embodiment, it is also known as centre valve.Yet it is embodied as acentric hydrovalve equally.Hydrovalve is embodied as plug-in mounting hydrovalve equally.

Fig. 3 is for only having shown electromagnetic adjusting element 134 for the acentric hydrovalve 112 of the hydraulic parts 113 shown in part.This adjust element 134 in inside by pressure balance.Therefore, passage 120 leads to the ring cavity 136 in adjusting element 134 by fuel-tank outlet T, and in this ring cavity, magnetic armature 135 is axially movably arranged.Magnetic armature 135 has recess 137, and magnetic armature 135 is by pressure balance thus.Because there is no conclusive pressure from fuel-tank outlet T, so having pressure and adjustment element 134 not to deviate from hydraulic part 113 ground, the space of magnetic armature 135 is not pressed.

Relatively, the hydraulic part two axial ends with the hydrovalve of supply interface P for example applies with supply pressure space with the order of P-B-T-A-P, thereby make to adjust element and hydrovalve, deviates from each other and is pressed.

Camshaft can be for example assembled cam shaft.

Fuel-tank outlet must not be arranged in distolateral.Therefore be possible equally as follows, that is, fuel-tank outlet is implemented as the radial hole in piston and/or in lining.

Hydrovalve is embodied as in rotor hub or the centre valve in the recess of the centre of camshaft.At this, camshaft can be assembled cam shaft, and cam is placed on pipe therein.

Electromagnetic adjusting element for centre valve in design must be according to Fig. 2.Especially be as follows possible, that is, prevent as follows the problem that the rotational motion due to abutment face 33 relative tappets 35 brings, that is, tappet 35 only abuts in abutment face 33 to point-like roundedly.Following is possible equally, that is, the end of tappet 35 is rolling bearing balls, and this rolling bearing ball abuts in abutment face 33.For example DE10 2,010 060 180A1 show like this for centre valve, with the electromagnetic adjusting element of rolling bearing ball.

Be alternatively possible equally as follows, that is, hydrovalve be implemented as to remote valve or be implemented as acentric hydrovalve.

For regulating the pressure of rotary actuator can be from fluid delivery pump.The oil pump that this fluid delivery pump can be supplied in particular for the lubricant medium of internal-combustion engine.If yet for the high governing speed of rotary actuator, should apply relatively high pressure, so fluid delivery pump only can attach troops to a unit in

Rotary actuator maybe can attach troops to a unit in

Rotary actuator and other hydraulic package.

In this case, fluid delivery pump is for example embodied as vane pump.Alternatively, gear pump, radial piston pump and crescent pump (Mondsichelpumpen) are possible.

Obviously, two working interfaces are arbitrarily and can exchange each other with the name of alphabetical A or B.

Piston can be produced by metal or by composite.Composite is manufactured in injection moulding mode.In using the situation of composite, fibre-reinforced composite is favourable equally, as it is shown in undocumented DE10 2,007 026 831.

In order to manufacture piston, can use the mould with slide block.

Described mode of execution is only exemplary design proposal.The combination of the described feature of different mode of executions is possible equally.The other feature of especially not describing that belongs to device part of the present invention is learnt by the geometrical construction illustrated in the accompanying drawings that installs part.

Claims

1. with the rotary actuator (14) of hydrovalve (12), the working interface (A, B) that hydrovalve has shoulder hole (28) and set out by shoulder hole, wherein, by pressure balanced box type piston (32), can be axially movably arranged in described hole (28) and install sealedly in bore section (71) with the first outer diameter (D3), wherein, described box type piston (32) is followed described the first outer diameter and is had

-with the enveloping surface (47) of large outer diameter (D2) and

-in the region of other working interface (B) with the enveloping surface (48) of little outer diameter (D1),

Being introduced in the disc (80) being formed by little outer diameter (D1) that supply pressure in the cavity (80) of described box type piston (32) is carried in projection on the one hand locates, thereby capable (F1) worked in the axial direction, and described supply pressure is carried in the anchor ring (61) of projection on the other hand, locate, it is deducted described the first outer diameter (D3) by described large outer diameter (D2) and forms.

2. the rotary actuator with hydrovalve (12) according to claim 1 (14), it is characterized in that, described box type piston (32) has in the axial region of the first working interface (A) enveloping surface (47) with large outer diameter (D2), corresponding inflow seamed edge (41 or 44) and outflow seamed edge (42 or 43) are set out by described two enveloping surfaces (47,48), wherein, described two flow into seamed edges (41,44) and deviate from each other and point to and described outflow seamed edge (42,43) points to relative to one another.

3. the rotary actuator with hydrovalve (12) according to claim 1 and 2 (14), is characterized in that, described supply pressure is carried on the disc (60) of described projection on whole.

4. according to the rotary actuator with hydrovalve (12) in any one of the preceding claims wherein (14), it is characterized in that, described disc (60) equals described anchor ring (61).

5. according to the rotary actuator with hydrovalve (12) in any one of the preceding claims wherein (14), it is characterized in that, described two working interfaces (B, A) are followed pressure medium interface (P), and described fuel-tank outlet (T) is followed pressure medium interface (P).

6. according to the rotary actuator with hydrovalve (12) described in any one in claim 1 to 4 (14), it is characterized in that, the first working interface (B) is followed pressure medium interface (P), fuel-tank outlet (T1) is followed the first working interface (B), and other working interface (A) is followed fuel-tank outlet (T1).

7. according to the rotary actuator with hydrovalve (12) in any one of the preceding claims wherein (14), it is characterized in that, the internal diameter (70) of locating in order to set up for the first outer diameter (D3) in bore section (71) is provided with sleeve pipe (64), it is fixedly inserted in described hole (28), thereby described box type piston (32) can be installed in described hole (28) before the time that described sleeve pipe (64) is installed.

8. according to the rotary actuator with hydrovalve (12) in any one of the preceding claims wherein (14), it is characterized in that, flow channel (37) is realized via the wall (40) extending obliquely haply in described box type piston (32) with the description of flow pass (38) in described box type piston (32), wherein, the extension part of described inclination is controlled seamed edge (41 by four, 42, 43, 44) separately, these control seamed edges are arranged in and radially deviate from the annular tab (45 that described box type piston extends (32), 46) on, wherein, annular tab (45) near described adjustment element (34) has the enveloping surface (47) with large outer diameter (D2), wherein, described annular tab (45) is directed in the region of large internal diameter (29) in the hole (28) at center, wherein, away from the annular tab (46) of described adjustment element (34), have in the hole (28) with enveloping surface (48) the Qie center of little outer diameter (D1) directed in the region of little internal diameter (30).

9. according to the rotary actuator with hydrovalve (12) described in claim 5 or 6 (14), it is characterized in that, described hydrovalve (12) is implemented as the centre valve in rotor hub (7), wherein, described supply pressure is axially fed to described box type piston (32) by the assembled cam shaft that is implemented as hollow tubular (16).

10. according to the rotary actuator with hydrovalve (12) described in any one in claim 1 to 8 (14), it is characterized in that, described hydrovalve (112) is implemented as acentric hydrovalve (112), and the adjustment element (134) of its electromagnetism has the magnetic armature (135) that band is useful on inner pressure balanced recess (137).

11. according to the rotary actuator with hydrovalve (12) in any one of the preceding claims wherein (14), it is characterized in that, described little outer diameter is four times of constant (K), wherein, described large outer diameter is five times of described constant (K), wherein, described the first outer diameter is three times of described constant (K).